EP0258114B1 - Torsion damping device for a torque transmissing system - Google Patents

Torsion damping device for a torque transmissing system Download PDF

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Publication number
EP0258114B1
EP0258114B1 EP87401805A EP87401805A EP0258114B1 EP 0258114 B1 EP0258114 B1 EP 0258114B1 EP 87401805 A EP87401805 A EP 87401805A EP 87401805 A EP87401805 A EP 87401805A EP 0258114 B1 EP0258114 B1 EP 0258114B1
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EP
European Patent Office
Prior art keywords
radial
flanges
above mentioned
damper device
torsional damper
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP87401805A
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German (de)
French (fr)
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EP0258114A1 (en
Inventor
Dominique Després
Jacques Paquin
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Valeo SE
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Valeo SE
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Publication of EP0258114A1 publication Critical patent/EP0258114A1/en
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Expired legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/64—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts
    • F16D3/66—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts the elements being metallic, e.g. in the form of coils
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/1232—Wound springs characterised by the spring mounting
    • F16F15/12326—End-caps for springs
    • F16F15/12333—End-caps for springs having internal abutment means

Definitions

  • the invention relates to a torsion damping device for a torque transmission system, such as a clutch; it relates more particularly to improvements made to certain elements of two coaxial parts mounted with the possibility of limited rotation relative to one another.
  • a torque transmission system such as a friction clutch, intended to be interposed between the crankshaft of the engine and the input shaft of the gearbox, in a motor vehicle, very generally comprises a torsional damping device capable of absorb variations in this torque, to prevent vibrations and in particular sound vibrations from occurring throughout the kinematic chain in which said torsion damping device is inserted.
  • a damping device is for example combined with the clutch friction disc or with the flywheel driven by the engine crankshaft and also acting as a reaction plate for the clutch.
  • French patent N ° 2571461 describes such a damping device combined with a flywheel.
  • the flywheel comprises two coaxial parts between which are arranged circumferentially arranged helical springs. More precisely, each spring is held between pedestals mounted articulated between two flanges (otherwise called guide washers) of a first part, in this case the driving part, while these same bases are liable to be circumferentially stressed with possibility of articulation, by annular sheets of sheet metal integral with the driven part, the variation of compression of the springs ensuring the absorption of the variations of torque and a certain filtering of vibrations of all kinds.
  • One of the aims of the invention is to reduce the operating noise in such a torsional damper.
  • Another object of the invention is to allow the flanges and sails of this torsional damper to be produced at a lower cost.
  • the invention therefore relates to a torsion damping device, in particular in a clutch, of the type comprising two coaxial parts mounted with the possibility of limited rotation relative to one another, a first part comprising two annular flanges substantially parallel and a second part comprising at least one veil interposed axially between the two flanges and springs disposed substantially circumferentially between bases mounted on one of the parts, each base comprising first engagement means cooperating with complementary engagement means of one of the parts and of the second engagement means cooperating with complementary engagement means of the other part, characterized in that said complementary engagement means of the flanges and / or of the veil (s) are constituted by inserts made of elastomer or synthetic material, for example relatively rigid molded plastic.
  • flywheel 11 forming a torsion damper 11, for motor vehicle transmission, this flywheel having an annular contact surface 12 suitable for making it play the additional role of reaction plate in a friction clutch.
  • the flywheel 11 is intended to be fixed by its hub 13 to the crankshaft of the internal combustion engine of the motor vehicle. It has two coaxial parts 15 and 16, which are ront respectively called below first and second parts, mounted with the possibility of limited rotation one with respect to the other against, in particular, the force exerted circumferentially between them by helical springs 18.
  • the first part 15 or driving part, of which the hub 13 is a part comprises two annular flanges 19, 20, made of metal, commonly called "guide washers".
  • the flange 19 is fixed to the hub 13.
  • the flange 20, parallel to the flange 19 is fixed externally to the latter with the interposition of a massive annular spacer 22 carrying the starter ring.
  • Elongated windows 23 are defined in these flanges, they extend circumferentially.
  • Each window of a flange is opposite a symmetrical window of the other flange so as to define housings suitable for housing the springs 18.
  • Each spring 18 is mounted in such a housing by means of two bases end 24.
  • Each base 24 comprises first engagement means cooperating with complementary engagement means of the flanges 19 and 20.
  • each base thus comprises two lateral pins 25 admitting a common axis parallel to the axis of rotation of the damping flywheel while the substantially radial edges of the windows 23 are provided with rounded notches 26 receiving the pins 25 of the corresponding base.
  • the center of each end of the spring 18 is positioned closer to the axis of rotation than the center of rotation of the pin 25.
  • the second part 16 is mounted in rotation on the hub 13 by a ball bearing 34 and consists of an annular part 35, forming a sort of hub and a plate 36, fixed to the annular part 35 by screws 37
  • This plate more particularly constitutes the clutch reaction plate since its external radial face forms the annular contact surface 12 on which the clutch friction is applied (not shown).
  • the annular part 35 and the plate 36 have respective radial annular bearing surfaces, 35a, 36a parallel while two parallel webs 38, 39, in cut sheet metal, are engaged in the space defined by these two annular bearing surfaces and pushed axially towards them, respectively, by elastic means with axial action, here in this case two Belleville washers 40, 41.
  • the bearing surface 35a is formed by means of a flange extending radially in the direction of the spacer 22, which has the part 35 which, moreover, centers the webs 38, 39.
  • Each web carries an annular friction lining 45 by which it is in frictional contact with the corresponding radial annular bearing.
  • the webs 38, 39 interposed axially between the two flanges 19, 20 are capable of cooperating with the bases 24 of the springs (in a manner which will be described in more detail below) and the arrangement which has just been described constitutes a torque limiter authorizing rotary sliding between said first and second coaxial parts, when the transmitted torque exceeds a predetermined value.
  • Each web 38, 39 has a flat annular part carrying the linings 45, extended outwards by radial arms 48 (as many as springs) subject to move circumferentially between the springs.
  • Each base therefore comprises second engagement means in the form of a recess 55 with a rounded bottom opening between the two pins 25 and cooperating with engagement means complementary to this second part, namely fingers 49, extending substantially circumferentially, carried by the arms 48.
  • engagement means complementary to this second part, namely fingers 49, extending substantially circumferentially, carried by the arms 48.
  • fingers are specific to the invention and will be described in detail below.
  • the bases 24 are made of molded plastic but carry blocks of elastomeric material 56 serving as elastic stops in the event of overtorque resulting in excessive compression of the springs.
  • the recess 55 opens substantially in the middle of the rear face of the base 24 and facets inclined relative to one another are defined on either side of said recess 55.
  • friction means 60 are provided between said coaxial parts.
  • These friction means consist of a friction washer 62 and a Belleville washer 66 forming a spring.
  • the friction washer 62 is immobilized in rotation relative to the first part 15 by axial tabs 63 engaged in holes in the flange 19. It carries a friction lining 64 applied axially against a shoulder 65 of the annular part 35 of the second part 16. The friction washer is urged towards said shoulder by the Belleville washer 66 bearing between it and the flange 19.
  • the complementary engagement means of the flanges and / or of the veil (s) are constituted by inserts made of elastomeric or synthetic material, for example of relatively rigid molded plastic.
  • first pieces 70 of synthetic material attached to radial portions 72 of said flanges to define the substantially radial edges of the windows 23.
  • the rounded notches 26 are therefore defined in these first parts 70, which simplifies the manufacture of the flanges 19.20.
  • These are substantially thicker than the flanges to which they are fixed, in particular in the vicinity of a rounded notch so that the total articulation surface between the notches 26 and the pins 25 of any base 24 is significantly increased. This results in better working conditions for the bases.
  • the surface condition of the edge of the notches 26, resulting from the molding is excellent.
  • the thickness flanges 19, 20 can be reduced since they no longer intervene in the contact surface with the bases.
  • each first part 70 above mentioned is in fact common to two adjacent windows 23 of the same flange. It thus comprises two relatively thick opposite parts 74a, 74b (each provided with a notch 26 corresponding respectively to two adjacent windows 23 of the flange) and a central mounting part 76 here comprising a recessed or thinned area of shape and dimensions corresponding to those of a radial portion 72 to be able to be embedded thereon.
  • the central part 76 is fixed to the radial portion 72 by a rivet 78.
  • a recess 75 In the vicinity of each rounded notch 26 is defined a recess 75 in the thickness of said first part, for the passage of the rear face of the corresponding base 24.
  • the radial face of the recess 75 is substantially in the extension of the internal face of the flange, for guiding continuity of the base when it leaves its supports 25, 26.
  • conforming accordingly that is to say according to the shape of the base) the edges of said first part in the vicinity of the notches 26, it is possible to substantially increase the contact surface at the end of articulation between each base and the first part 70, more precisely between the latter and the aforementioned heel, which reduces wear and tear on these parts while reducing noise.
  • the cutouts defining the windows 23 in the flanges 19, 20 are circumferentially extended to allow the embedding of the parts 74a, 74b in the thickness of the flange, so as to define the circumferential ends of the windows 23.
  • each first part 70 admits a median plane of symmetry, which makes it possible to have only one type of part, in production, capable of being mounted either on the flange 19 or 20.
  • each radial arm 48 mentioned above consists of a simple radial tab 80 cut out of the metal veil itself and, for at least certain radial tabs, of at least one second piece 82 of elastomeric or synthetic material, relatively rigid, fixed on said radial tab 80 and shaped to define laterally at least one finger 49 whose rounded end is capable of coming into articulated contact with the bottom of a recess 55 d a corresponding base 24.
  • each second part 82 comprises two opposite fingers 49, connected to a central part in which is defined a thinned zone comprising at least a first radial groove 83 of shape and dimensions corresponding to those of a radial tab 80.
  • each piece 82 has two portions inclined relative to each other, on either side of the corresponding finger 49 to cooperate with the inclined facets of the corresponding base.
  • the contact surface between each finger of elastomeric or synthetic material and the bottom of the recess 55 is significantly increased compared to that obtained with the known prior arrangement where contact does not occur. was only by the edge of the fingers, directly cut from the sheet of the sails. It is the same, at the end of articulation, between said substantially radial edges and said facets.
  • each second part 82 may comprise, in its thinned zone, a second radial groove 86 opposite to the groove 82 by which said second part is fixed to one sails.
  • the second groove 86 is of shape and dimensions corresponding to another radial tab 88 of the other sail.
  • the rivet 84 has two countersunk heads, but a normal head could also be provided on the side of the radial tab 88, leaving a corresponding hole in the latter, to house the rivet head.
  • the radial tab 88 is freely embedded (that is to say engaged with the possibility of displacement parallel to the axis of the device) in said second groove 86.
  • the two webs 38, 39 are thus held circumferentially in correct correspondence, any rotation relative from one to the other being prevented by the shape connections defined at the level of said second parts 82.
  • the web which is engaged in a said second groove 86 can move axially to compensate for the wear of the linings 45, without being able to escape from this groove.
  • Said second pieces can all be fixed to one of the sails; it is also possible to attach such a second part to one of two radial lugs, for each sail. In the latter case, the two sails are then strictly identical in manufacture.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Fluid-Damping Devices (AREA)

Description

L'invention se rapporte à un dispositif amortisseur de torsion pour système de transmission de couple, tel qu'un embrayage; elle concerne plus particulièrement des perfectionnements apportés à certains éléments de deux parties coaxiales montées avec possibilité de rotation limitée l'une par rapport à l'autre.The invention relates to a torsion damping device for a torque transmission system, such as a clutch; it relates more particularly to improvements made to certain elements of two coaxial parts mounted with the possibility of limited rotation relative to one another.

Un système de transmission de couple tel qu'un embrayage à friction, destiné à être intercalé entre le vilebrequin du moteur et l'arbre d'entrée de la boîte de vitesses, dans un véhicule automobile, comporte très généralement un dispositif amortisseur de torsion susceptible d'absorber les variations de ce couple, pour éviter que des vibrations et en particulier des vibrations sonores ne prennent naissance tout au long de la chaîne cinématique dans laquelle ledit dispositif amortisseur de torsion est inséré. Un tel dispositif amortisseur est par exemple combiné au disque de friction de l'embrayage ou au volant d'inertie entraîné par le vilebrequin du moteur et faisant également fonction de plateau de réaction pour l'embrayage.A torque transmission system such as a friction clutch, intended to be interposed between the crankshaft of the engine and the input shaft of the gearbox, in a motor vehicle, very generally comprises a torsional damping device capable of absorb variations in this torque, to prevent vibrations and in particular sound vibrations from occurring throughout the kinematic chain in which said torsion damping device is inserted. Such a damping device is for example combined with the clutch friction disc or with the flywheel driven by the engine crankshaft and also acting as a reaction plate for the clutch.

Ainsi, le brevet français N° 2571461 décrit un tel dispositif amortisseur combiné à un volant d'inertie. Le volant comprend deux parties coaxiales entre lesquelles sont agencés des ressorts hélicoïdaux disposés circonférentiellement. Plus précisément, chaque ressort est maintenu entre des socles montés articulés entre deux flasques (autrement appelés rondelles de guidage) d'une première partie, en l'occurrence la partie menante, tandis que ces mêmes socles sont susceptibles d'être sollicités circonférentiellement avec possibilité d'articulation, par des voiles annulaires en tôle solidaires de la partie menée, la variation de compression des ressorts assurant l'absorption des variations de couple et un certain filtrage des vibrations de toutes sortes.Thus, French patent N ° 2571461 describes such a damping device combined with a flywheel. The flywheel comprises two coaxial parts between which are arranged circumferentially arranged helical springs. More precisely, each spring is held between pedestals mounted articulated between two flanges (otherwise called guide washers) of a first part, in this case the driving part, while these same bases are liable to be circumferentially stressed with possibility of articulation, by annular sheets of sheet metal integral with the driven part, the variation of compression of the springs ensuring the absorption of the variations of torque and a certain filtering of vibrations of all kinds.

Ce système donne de bons résultats, principalement en raison de la présence des socles articulés qui permettent aux ressorts de fonctionner dans de meilleures conditions en évitant qu'ils ne soient soumis à des déformations radiales excessives, vers l'intérieur ou l'extérieur. Cependant, les chocs entre les socles d'une part et les flasques et voiles d'autre part sont relativement audibles. En outre, lesdits socles étant en matière plastique moulée, les parties des flasques et voiles qui coopèrent avec lesdits socles doivent faire l'objet d'un découpage précis, exempt de toute bavure, pour ne pas provoquer une détérioration des zones des socles avec lesquelles elles s'articulent. La fabrication des fiasques et des voiles est donc relativement coûteuse, puisqu'elle ne peut consister en un simple découpage à l'emporte-pièce.This system gives good results, mainly due to the presence of articulated bases which allow the springs to function in better conditions preventing them from being subjected to excessive radial deformations, inwards or outwards. However, the shocks between the bases on the one hand and the flanges and sails on the other are relatively audible. In addition, said bases being of molded plastic, the parts of the flanges and sails which cooperate with said bases must be cut precisely, free from any burr, so as not to cause deterioration of the areas of the bases with which they are articulated. The manufacture of flasks and sails is therefore relatively expensive, since it cannot consist of a simple die-cutting.

L'un des buts de l'invention est de réduire les bruits de fonctionnement dans un tel amortisseur de torsion.One of the aims of the invention is to reduce the operating noise in such a torsional damper.

Un autre but de l'invention est de permettre de réaliser les flasques et voiles de cet amortisseur de torsion à moindre coût.Another object of the invention is to allow the flanges and sails of this torsional damper to be produced at a lower cost.

Dans ces buts, l'invention concerne donc un dispositif amortisseur de torsion, notamment dans un embrayage, du type comportant deux parties coaxiales montées avec possibilité de rotation limitée l'une par rapport à l'autre, une première partie comportant deux flasques annulaires sensiblement parallèles et une seconde partie comportant au moins un voile intercalé axialement entre les deux flasques et des ressorts diposés sensiblement circonférentiellement entre des socles montés sur l'une des parties, chaque socle comportant des premiers moyens d'engagement coopérant avec des moyens d'engagement complémentaires de l'une des parties et des seconds moyens d'engagement coopérant avec des moyens d'engagement complémentaires de l'autre partie, caractérisé en ce que lesdits moyens d'engagement complémentaires des flasques et/ou du ou des voiles sont constitués par des pièces rapportées en élastomère ou en matériau synthétique, par exemple en matière plastique moulée relativement rigide.For these purposes, the invention therefore relates to a torsion damping device, in particular in a clutch, of the type comprising two coaxial parts mounted with the possibility of limited rotation relative to one another, a first part comprising two annular flanges substantially parallel and a second part comprising at least one veil interposed axially between the two flanges and springs disposed substantially circumferentially between bases mounted on one of the parts, each base comprising first engagement means cooperating with complementary engagement means of one of the parts and of the second engagement means cooperating with complementary engagement means of the other part, characterized in that said complementary engagement means of the flanges and / or of the veil (s) are constituted by inserts made of elastomer or synthetic material, for example relatively rigid molded plastic.

Les bruits de fonctionnement sont réduits par le fait que les parties qui entrent en contact avec les socles ne sont plus en métal mais en matériau moins "sonore". En outre, la surface de contact entre ces éléments rapportés et les socles peut être notablement augmentée par rapport à ce qu'elle était antérieurement, lorsque les flasques et les voiles coopéraient avec lesdits socles uniquement par leur tranche. Enfin, il devient facile d'obtenir des surfaces d'articulation de bonne qualité, au moulage des pièces rapportées, ces dernières pouvant être fixées sans inconvénient à des parties des voiles et/ou flasques présentant des bords provenant d'un découpage non rectifié.Operating noise is reduced by the fact that the parts which come into contact with the bases are no longer made of metal but of less "sound" material. In addition, the contact surface between these added elements and the bases can be significantly increased compared to what it was previously, when the flanges and the sails cooperated with said bases only by their edges. Finally, it becomes easy to obtain articulation surfaces of good quality, by molding the added parts, the latter being able to be fixed without disadvantage to parts of the webs and / or flanges having edges coming from an unrefined cutting.

L'invention sera mieux comprise et d'autres avantages de celle-ci apparaîtront plus clairement à la lumière de la description qui va suivre d'un dispositif amortisseur de torsion conforme à son principe, donnée uniquement à titre d'exemple et faite en référence aux dessins annexés dans lesquels:

  • - la figure 1 est une vue d'ensemble du dispositif amortisseur de torsion représenté selon la coupe I-I de la figure 2;
  • - la figure 2 est une vue partielle et avec arrachement du même dispositif vu selon la flèche Il de la figure 1;
  • - la figure 3 est une vue partielle avec arrachement, selon la. flèche III de la figure 2 et illustrant plus particulièrement les voiles de la seconde partie précitée; et
  • - la figure 4 est une coupe partielle IV-IV de la figure 2 montrant plus particulièrement les moyens de l'invention au niveau d'un flasque de la première partie précitée.
The invention will be better understood and other advantages thereof will appear more clearly in the light of the following description of a torsion damping device in accordance with its principle, given solely by way of example and made with reference to the accompanying drawings in which:
  • - Figure 1 is an overview of the torsion damping device shown in section II of Figure 2;
  • - Figure 2 is a partial view with parts broken away of the same device seen according to arrow II in Figure 1;
  • - Figure 3 is a partial view with cutaway, according to the. arrow III of Figure 2 and illustrating more particularly the sails of the aforementioned second part; and
  • - Figure 4 is a partial section IV-IV of Figure 2 showing more particularly the means of the invention at a flange of the aforementioned first part.

En se reportant aux dessins, on a représenté plus particulièrement un volant d'inertie formant amortisseur de torsion 11, pour transmission de véhicule automobile, ce volant comportant une surface annulaire de contact 12 propre à lui faire jouer le rôle supplémentaire de plateau de réaction dans un embrayage à friction. A ce titre, le volant 11 est destiné à être fixé par son moyeu 13 au vilebrequin du moteur à combustion interne du véhicule automobile. Il comporte deux parties coaxiales 15 et 16, qui seront respectivement appelées ci-dessous première et seconde parties, montées avec possibilité de rotation limitée l'une par rapport à l'autre à l'encontre, notamment, de la force exercée circonférentiellement entre elles par des ressorts hélicoïdaux 18. La première partie 15 ou partie menante, dont fait partie le moyeu 13, comporte deux flasques annulaires 19, 20, métalliques, communément appelés "rondelles de guidage". Le flasque 19 est fixé au moyeu 13. Le flasque 20, parallèle au flasque 19 est fixé extérieurement à celui-ci avec interposition d'une entretoise annulaire massive 22 portant la couronne de démarreur. Des fenêtres 23 allongées sont définies dans ces flasques, elles s'étendent circonférentiellement. Chaque fenêtre d'un flasque est en regard d'une fenêtre symétrique de l'autre flasque de façon à définir des logements propres à abriter les ressorts 18. Chaque ressort 18 est monté dans un tel logement par l'intermédiaire de deux socles d'extrémité 24. Chaque socle 24 comporte des premiers moyens d'engagement coopérant avec des moyens d'engagement complémentaires des flasques 19 et 20. Dans l'exemple décrit, chaque socle comporte ainsi deux tourillons latéraux 25 admettant un axe commun parallèle à l'axe de rotation du volant amortisseur tandis que les bords sensiblement radiaux des fenêtres 23 sont pourvus d'encoches arrondies 26 recevant les tourillons 25 du socle correspondant. En pratique également, le centre de chaque extrémité du ressort 18 est positionné plus près de l'axe de rotation que le centre de rotation du tourillon 25.Referring to the drawings, there is shown more particularly a flywheel forming a torsion damper 11, for motor vehicle transmission, this flywheel having an annular contact surface 12 suitable for making it play the additional role of reaction plate in a friction clutch. As such, the flywheel 11 is intended to be fixed by its hub 13 to the crankshaft of the internal combustion engine of the motor vehicle. It has two coaxial parts 15 and 16, which are ront respectively called below first and second parts, mounted with the possibility of limited rotation one with respect to the other against, in particular, the force exerted circumferentially between them by helical springs 18. The first part 15 or driving part, of which the hub 13 is a part, comprises two annular flanges 19, 20, made of metal, commonly called "guide washers". The flange 19 is fixed to the hub 13. The flange 20, parallel to the flange 19 is fixed externally to the latter with the interposition of a massive annular spacer 22 carrying the starter ring. Elongated windows 23 are defined in these flanges, they extend circumferentially. Each window of a flange is opposite a symmetrical window of the other flange so as to define housings suitable for housing the springs 18. Each spring 18 is mounted in such a housing by means of two bases end 24. Each base 24 comprises first engagement means cooperating with complementary engagement means of the flanges 19 and 20. In the example described, each base thus comprises two lateral pins 25 admitting a common axis parallel to the axis of rotation of the damping flywheel while the substantially radial edges of the windows 23 are provided with rounded notches 26 receiving the pins 25 of the corresponding base. In practice also, the center of each end of the spring 18 is positioned closer to the axis of rotation than the center of rotation of the pin 25.

La seconde partie 16 est montée en rotation sur le moyeu 13 par un roulement à billes 34 et se compose d'une pièce annulaire 35, formant une sorte de moyeu et d'un plateau 36, fixé à la pièce annulaire 35 par des vis 37. Ce plateau constitue plus particulièrement le plateau de réaction de l'embrayage puisque sa face radiale externe forme la surface annulaire de contact 12 sur laquelle vient s'appliquer la friction d'embrayage (non représentée).The second part 16 is mounted in rotation on the hub 13 by a ball bearing 34 and consists of an annular part 35, forming a sort of hub and a plate 36, fixed to the annular part 35 by screws 37 This plate more particularly constitutes the clutch reaction plate since its external radial face forms the annular contact surface 12 on which the clutch friction is applied (not shown).

D'autre part, la pièce annulaire 35 et le plateau 36 comportent des portées annulaires radiales respectives, 35a, 36a parallèles tandis que deux voiles parallèles 38, 39, en tôle découpée, sont engagés dans l'espace défini par ces deux portées annulaires et repoussés axialement vers celles-ci, respectivement, par des moyens élastiques à action axiale, ici en l'occurrence deux rondelles Belleville 40, 41. Ici, la portée 35a est formée à la faveur d'une bride s'étendant radialement en direction de l'entretoise 22, que possède la pièce 35 qui, par ailleurs, centre les voiles 38, 39. Chaque voile porte une garniture de friction annulaire 45 par laquelle il est en contact frottant avec la portée annulaire radiale correspondante. Les voiles 38, 39 intercalés axialement entre les deux flasques 19, 20 sont susceptibles de coopérer avec les socles 24 des ressorts (d'une façon qui sera décrite plus en détail ci-dessous) et l'agencement qui vient d'être décrit constitue un limiteur de couple autorisant un glissement rotatif entre lesdites première et seconde parties coaxiales, lorsque le couple transmis dépasse une valeur prédéterminée. Chaque voile 38, 39 comporte une partie annulaire plate portant les garnitures 45, prolongée vers l'extérieur par des bras radiaux 48 (autant que de ressorts) assujettis à se déplacer circonférentiellement entre les ressorts. Chaque socle comporte donc des seconds moyens d'engagement sous forme d'une creusure 55 à fond arrondi ouvrant entre les deux tourillons 25 et coopérant avec des moyens d'engagement complémentaires de cette seconde partie, à savoir des doigts 49, s'étendant sensiblement circonférentiellement, portés par les bras 48. Ces doigts sont spécifiques de l'invention et seront décrits en détail plus loin. Les socles 24 sont en matière plastique moulée mais portent des blocs de matériau élastomère 56 servant de butées élastiques en cas de surcouples aboutissant à une compression excessive des ressorts.On the other hand, the annular part 35 and the plate 36 have respective radial annular bearing surfaces, 35a, 36a parallel while two parallel webs 38, 39, in cut sheet metal, are engaged in the space defined by these two annular bearing surfaces and pushed axially towards them, respectively, by elastic means with axial action, here in this case two Belleville washers 40, 41. Here, the bearing surface 35a is formed by means of a flange extending radially in the direction of the spacer 22, which has the part 35 which, moreover, centers the webs 38, 39. Each web carries an annular friction lining 45 by which it is in frictional contact with the corresponding radial annular bearing. The webs 38, 39 interposed axially between the two flanges 19, 20 are capable of cooperating with the bases 24 of the springs (in a manner which will be described in more detail below) and the arrangement which has just been described constitutes a torque limiter authorizing rotary sliding between said first and second coaxial parts, when the transmitted torque exceeds a predetermined value. Each web 38, 39 has a flat annular part carrying the linings 45, extended outwards by radial arms 48 (as many as springs) subject to move circumferentially between the springs. Each base therefore comprises second engagement means in the form of a recess 55 with a rounded bottom opening between the two pins 25 and cooperating with engagement means complementary to this second part, namely fingers 49, extending substantially circumferentially, carried by the arms 48. These fingers are specific to the invention and will be described in detail below. The bases 24 are made of molded plastic but carry blocks of elastomeric material 56 serving as elastic stops in the event of overtorque resulting in excessive compression of the springs.

En pratique, la creusure 55 s'ouvre sensiblement au milieu de la face arrière du socle 24 et des facettes inclinées l'une par rapport à l'autre sont définies de part et d'autre de ladite creusure 55.In practice, the recess 55 opens substantially in the middle of the rear face of the base 24 and facets inclined relative to one another are defined on either side of said recess 55.

Entre lesdites facettes et les tourillons 25 sont définis des talons, l'écartement entre deux talons correspondant à la largeur de la creusure.Between said facets and the pins 25 are defined heels, the spacing between two heels corresponding to the width of the recess.

Comme le montrent les dessins, les ressorts n'interviennent pas dès le début du débattement angulaire entre les deux parties coaxiales, puisque les bras radiaux doivent effectuer une certaine course angulaire avant que certains de leurs doigts ne s'engagent dans les creusures des socles correspondants. Avant l'engagement desdits doigts au fond desdits socles, des moyens de frottement 60 (intervenant quant à eux dès le début du débattement angulaire entre les deux parties coaxiales) sont prévus entre lesdites parties coaxiales. Ces moyens de frottement se composent d'une rondelle de frottement 62 et d'une rondelle Belleville 66 formant ressort. La rondelle de frottement 62 est immobilisée en rotation par rapport à la première partie 15 par des pattes axiales 63 engagées dans des trous du flasque 19. Elle porte une garniture de friction 64 appliquée axialement contre un épaulement 65 de la pièce annulaire 35 de la seconde partie 16. La rondelle de frottement est sollicitée vers ledit épaulement par la rondelle Belleville 66 prenant appui entre celle-ci et le flasque 19.As the drawings show, the springs do not intervene from the start of the angular movement between the two coaxial parts, since the radial arms must perform a certain angular stroke before some of their fingers engage in the recesses of the corresponding bases . Before the engagement of said fingers at the bottom of said bases, friction means 60 (intervening for their part from the start of the angular movement between the two coaxial parts) are provided between said coaxial parts. These friction means consist of a friction washer 62 and a Belleville washer 66 forming a spring. The friction washer 62 is immobilized in rotation relative to the first part 15 by axial tabs 63 engaged in holes in the flange 19. It carries a friction lining 64 applied axially against a shoulder 65 of the annular part 35 of the second part 16. The friction washer is urged towards said shoulder by the Belleville washer 66 bearing between it and the flange 19.

Selon l'invention, les moyens d'engagement complémentaires des flasques et/ou du ou des voiles sont constitués par des pièces rapportées en matériau élastomère ou synthétique, par exemple en matière plastique moulée relativement rigide. Ainsi, pour ce qui concerne les flasques 19, 20, on a prévu des premières pièces 70 en matériau synthétique, rapportées sur des portions radiales 72 desdits flasques pour définir les bords sensiblement radiaux des fenêtres 23. Les encoches arrondies 26 sont donc définies dans ces premières pièces 70, ce qui simplifie la fabrication des flasques 19,20. Celles-ci sont sensiblement plus épaisses que les flasques auxquels elles sont fixées, notamment au voisinage d'une encoche arrondie de sorte que la surface totale d'articulation entre encoches 26 et tourillons 25 d'un socle 24 quelconque, se trouve notablement augmentée. Il en résulte de meilleures conditions de travail pour les socles. De plus, l'état de surface de la tranche des encoches 26, résultant du moulage, est excellent. Enfin, l'épaisseur des flasques 19, 20 peut être réduite puisqu'ils n'interviennent plus dans la surface de contact avec les socles.According to the invention, the complementary engagement means of the flanges and / or of the veil (s) are constituted by inserts made of elastomeric or synthetic material, for example of relatively rigid molded plastic. Thus, as regards the flanges 19, 20, there are provided first pieces 70 of synthetic material, attached to radial portions 72 of said flanges to define the substantially radial edges of the windows 23. The rounded notches 26 are therefore defined in these first parts 70, which simplifies the manufacture of the flanges 19.20. These are substantially thicker than the flanges to which they are fixed, in particular in the vicinity of a rounded notch so that the total articulation surface between the notches 26 and the pins 25 of any base 24 is significantly increased. This results in better working conditions for the bases. In addition, the surface condition of the edge of the notches 26, resulting from the molding, is excellent. Finally, the thickness flanges 19, 20 can be reduced since they no longer intervene in the contact surface with the bases.

Comme cela apparaît clairement à la figure 2, chaque première pièce 70 précitée est en fait commune à deux fenêtres 23 adjacentes d'un même flasque. Elle comporte ainsi deux parties opposées 74a, 74b relativement épaisses (munies, chacune, d'une encoche 26 correspondant respectivement à deux fenêtres adjacentes 23 du flasque) et une partie centrale de montage 76 comportant ici une zone en creux ou amincie de forme et dimensions correspondant à celles d'une portion radiale 72 pour pouvoir s'encastrer sur celle-ci. La partie centrale 76 est fixée à la portion radiale 72 par un rivet 78. Au voisinage de chaque encoche arrondie 26 est défini un décrochement 75 dans l'épaisseur de ladite première pièce, pour le passage de la face arrière du socle 24 correspondant. La face radiale du décrochement 75 est sensiblement dans le prolongement de la face interne du flasque, pour continuité de guidage du socle lorsqu'il quitte ses appuis 25, 26. Ainsi, en conformant en conséquence (c'est-à-dire en fonction de la forme du socle) les bords de ladite première pièce au voisinage des encoches 26, on peut augmenter sensiblement la surface de contact en fin d'articulation entre chaque socle et la première pièce 70, plus précisément entre cette dernière et le talon précité, ce qui réduit l'usure de ces pièces tout en atténuant le bruit. Les découpes définissant les fenêtres 23 dans les flasques 19, 20 sont prolongées circonférentiellement pour permettre l'encastrement des parties 74a, 74b dans l'épaisseur du flasque, de façon à définir les extrémités circonférentielles des fenêtres 23. De plus, chaque première pièce 70 admet un plan de symétrie médian, ce qui permet de ne disposer que d'un seul type de pièce, en fabrication, susceptible d'être monté indifféremment sur le flasque 19 ou 20.As clearly appears in FIG. 2, each first part 70 above mentioned is in fact common to two adjacent windows 23 of the same flange. It thus comprises two relatively thick opposite parts 74a, 74b (each provided with a notch 26 corresponding respectively to two adjacent windows 23 of the flange) and a central mounting part 76 here comprising a recessed or thinned area of shape and dimensions corresponding to those of a radial portion 72 to be able to be embedded thereon. The central part 76 is fixed to the radial portion 72 by a rivet 78. In the vicinity of each rounded notch 26 is defined a recess 75 in the thickness of said first part, for the passage of the rear face of the corresponding base 24. The radial face of the recess 75 is substantially in the extension of the internal face of the flange, for guiding continuity of the base when it leaves its supports 25, 26. Thus, conforming accordingly (that is to say according to the shape of the base) the edges of said first part in the vicinity of the notches 26, it is possible to substantially increase the contact surface at the end of articulation between each base and the first part 70, more precisely between the latter and the aforementioned heel, which reduces wear and tear on these parts while reducing noise. The cutouts defining the windows 23 in the flanges 19, 20 are circumferentially extended to allow the embedding of the parts 74a, 74b in the thickness of the flange, so as to define the circumferential ends of the windows 23. In addition, each first part 70 admits a median plane of symmetry, which makes it possible to have only one type of part, in production, capable of being mounted either on the flange 19 or 20.

Pour ce qui concerne les voiles 38,39, chaque bras radial 48 mentionné ci-dessus se compose d'une simple patte radiale 80 découpée dans le voile métallique proprement dit et, pour au moins certaines pattes radiales, d'au moins une seconde pièce 82 en matériau élastomère ou synthétique, relativement rigide, fixée sur ladite patte radiale 80 et conformée pour y définir latéralement au moins un doigt 49 dont l'extrémité arrondie est susceptible d'entrer en contact articulé avec le fond d'une creusure 55 d'un socle 24 correspondant. Selon l'exemple, chaque seconde pièce 82 comporte deux doigts 49 opposés, raccordés à une partie médiane dans laquelle est définie une zone amincie comportant au moins une première rainure radiale 83 de forme et dimensions correspondant à celles d'une patte radiale 80. Cette première rainure permet donc l'encastrement de la pièce 82 sur la patte radiale 80 correspondante. La pièce 82 est en outre fixée à ladite patte radiale par un rivet 84 ou un moyen analogue. Outre les doigts 49, les bords sensiblement radiaux de chaque pièce 82 comportent deux portions inclinées l'une par rapport à l'autre, de part et d'autre du doigt 49 correspondant pour coopérer avec les facettes inclinées du socle correspondant. Comme cela est visible sur la figure 3, là encore, la surface de contact entre chaque doigt en matériau élastomère ou synthétique et le fond de la creusure 55 est sensiblement augmentée par rapport à celle obtenue avec l'agencement antérieur connu où le contact ne se faisait que par la tranche des doigts, directement découpés dans la tôle des voiles. Il en est de même, en fin d'articulation, entre lesdits bords sensiblement radiaux et lesdites facettes. Si le dispositif ne comporte pas de système de limitation de couple conforme à celui qui est représenté, un seul voile portant lesdites secondes pièces 82 est suffisant. Si en revanche, le système comporte un tel limiteur de couple nécessitant deux voiles parallèles, chaque seconde pièce 82 peut comporter, dans sa zone amincie, une seconde rainure radiale 86 opposée à la rainure 82 par laquelle ladite seconde pièce est fixée à l'un des voiles. La seconde rainure 86 est de forme et dimensions correspondant à une autre patte radiale 88 de l'autre voile. Dans l'exemple, le rivet 84 comporte deux têtes fraisées mais on pourrait aussi prévoir une tête normale du côté de la patte radiale 88 en ménageant un trou correspondant dans celle-ci, pour abriter la tête de rivet. La patte radiale 88 est librement encastrée (c'est-à-dire engagée avec possibilité de déplacement parallèlement à l'axe du dispositif) dans ladite seconde rainure 86. Les deux voiles 38, 39 sont ainsi maintenus circonférentiellement en correspondance correcte, toute rotation relative de l'un par rapport à l'autre étant empêchée par les liaisons de forme définies au niveau desdites secondes pièces 82. Le voile qui est engagé dans une sus-dite seconde rainure 86 peut se déplacer axialement pour compenser l'usure des garnitures 45, sans pouvoir pour autant s'échapper de cette rainure. Lesdites secondes pièces peuvent être toutes fixées à l'un des voiles; on peut aussi fixer une telle seconde pièce à une patte radiale sur deux, pour chaque voile. Dans ce dernier cas, les deux voiles sont alors rigoureusement identiques en fabrication.As regards the sails 38, 39, each radial arm 48 mentioned above consists of a simple radial tab 80 cut out of the metal veil itself and, for at least certain radial tabs, of at least one second piece 82 of elastomeric or synthetic material, relatively rigid, fixed on said radial tab 80 and shaped to define laterally at least one finger 49 whose rounded end is capable of coming into articulated contact with the bottom of a recess 55 d a corresponding base 24. According to the example, each second part 82 comprises two opposite fingers 49, connected to a central part in which is defined a thinned zone comprising at least a first radial groove 83 of shape and dimensions corresponding to those of a radial tab 80. This first groove therefore allows the fitting of the part 82 on the corresponding radial tab 80. The part 82 is also fixed to said radial tab by a rivet 84 or similar means. In addition to the fingers 49, the substantially radial edges of each piece 82 have two portions inclined relative to each other, on either side of the corresponding finger 49 to cooperate with the inclined facets of the corresponding base. As can be seen in FIG. 3, here again, the contact surface between each finger of elastomeric or synthetic material and the bottom of the recess 55 is significantly increased compared to that obtained with the known prior arrangement where contact does not occur. was only by the edge of the fingers, directly cut from the sheet of the sails. It is the same, at the end of articulation, between said substantially radial edges and said facets. If the device does not include a torque limiting system in accordance with that shown, a single web bearing said second parts 82 is sufficient. If, on the other hand, the system includes such a torque limiter requiring two parallel webs, each second part 82 may comprise, in its thinned zone, a second radial groove 86 opposite to the groove 82 by which said second part is fixed to one sails. The second groove 86 is of shape and dimensions corresponding to another radial tab 88 of the other sail. In the example, the rivet 84 has two countersunk heads, but a normal head could also be provided on the side of the radial tab 88, leaving a corresponding hole in the latter, to house the rivet head. The radial tab 88 is freely embedded (that is to say engaged with the possibility of displacement parallel to the axis of the device) in said second groove 86. The two webs 38, 39 are thus held circumferentially in correct correspondence, any rotation relative from one to the other being prevented by the shape connections defined at the level of said second parts 82. The web which is engaged in a said second groove 86 can move axially to compensate for the wear of the linings 45, without being able to escape from this groove. Said second pieces can all be fixed to one of the sails; it is also possible to attach such a second part to one of two radial lugs, for each sail. In the latter case, the two sails are then strictly identical in manufacture.

Claims (8)

1. A torsional damper device, especially for a clutch, of the kind comprising two coaxial parts (15, 16) mounted with the possibility of a limited degree of rotation relative to each other, a first part comprising two substantially parallel annular flanges (19, 20) and a second part comprising at least one plate (38, 39) disposed axially between the two flanges, and springs (18) disposed substantially circumferentially between base members (24) mounted on one of the parts, each base member comprising first engagement means cooperating with complementary engagement means on one of the parts and second engagement means cooperating with complementary engagement means on the other part, characterized in that the said complementary engagement means of the flanges and/or of the plate or plates consist of attached separate pieces (70, 82) made of an elastomer or synthetic material, for example of relatively rigid moulded plastic.
2. A torsional damper device according to Claim 1, of the kind in which the two above mentioned flanges comprise circumferentially elongated windows (23), two facing windows made respectively in the two flanges accommodate a spring (18), the said base members (24) are pivotably mounted between the two flanges at the ends of the said windows and each base member is equipped with journal members (25) which pivot in rounded notches (26) disposed on two substantially radial edges of the said facing windows, characterized in that above mentioned first separate pieces (70) made of an elastomer or synthetic material are attached to radial portions (72) of the said flanges to form the substantially radial edges of the said windows, the said first pieces (70) comprising the said rounded notches.
3. A torsional damper device according to Claim 2, characterized in that the thickness of a rounded notch (26) is greater than that of the flange (19, 20) which carries the said first piece in which the said notch is formed.
4. A torsional damper device according to Claim 2 or 3, characterized in that each of the above mentioned first separate pieces made of an elastomer or synthetic material comprises two opposed parts (74_a, 742) each incorporating a rounded notch, corresponding respectively to two adjacent windows (23) of the same flange, and a central mounting part (76) preferably comprising an area of reduced thickness having a shape and size corresponding to those of one of the above mentioned radial portions, the said central mounting part being attached (78) to such a radial portion (72).
5. A torsional damper device according to one of the preceding Claims, of the kind in which at least one of the above mentioned plates (38, 39) comprises radial arms each having oppositely directed substantially circumferential fingers, each finger (48) being adapted to make pivoting contact, by means of a rounded end, with a hollow (55) having a rounded bottom in an above mentioned base member, characterized in that the second pieces made of an elastomer or synthetic material (82) are attached to the radial arms of the said plate and are shaped to define at least the said fingers there.
6. A torsional damper device according to Claim 5, characterized in that each second piece (82) made of an elastomer or synthetic material comprises two of the said oppositely directed fingers (49) attached to a central part which incorporates an area of reduced thickness comprising a first radial groove (83) having a shape and size corresponding to those of a radial lug (80) on the said plate, the said separate piece being engaged and fixed on the said lug by this first groove.
7. A torsional damper device according to Claim 6 of the kind comprising two parallel plates (38, 39) between which spring means (40, 41) are disposed which push the said plates apart towards respective parallel bearing surfaces on the said second part (16), preferably with friction facings (45) being interposed, this arrangement constituting a torque limiter, characterized in that the above mentioned area of reduced thickness of each second piece (82) made of an elastomer or synthetic material comprises a second groove (86) opposed to the said first groove (83) by which it is fixed to one of the said plates, and in that the said second groove has a shape and size corresponding to those of a radial lug (88) on the other plate, such a radial lug being freely inserted in the said second groove.
8. A torsional damper device according to Claim 4, characterized in that each above mentioned first separate piece (70) has a median plane of symmetry.
EP87401805A 1986-08-21 1987-08-03 Torsion damping device for a torque transmissing system Expired EP0258114B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8611937 1986-08-21
FR8611937A FR2603083B1 (en) 1986-08-21 1986-08-21 TORSION DAMPING DEVICE FOR TORQUE TRANSMISSION SYSTEM

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EP0258114A1 EP0258114A1 (en) 1988-03-02
EP0258114B1 true EP0258114B1 (en) 1989-10-04

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EP (1) EP0258114B1 (en)
JP (1) JP2832601B2 (en)
DE (1) DE3760688D1 (en)
FR (1) FR2603083B1 (en)

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FR2583486B1 (en) * 1985-06-14 1989-03-31 Valeo TORSION DAMPING DEVICE, ESPECIALLY FOR A CLUTCH OF A MOTOR VEHICLE, WITH DAMPING AT LEAST PARTIALLY FROM AN ELASTOMERIC ELEMENT
JPH06159024A (en) * 1992-11-26 1994-06-07 Fuji Heavy Ind Ltd Air spring type valve system of engine for vehicle

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Publication number Publication date
JPS6353334A (en) 1988-03-07
JP2832601B2 (en) 1998-12-09
US4820239A (en) 1989-04-11
DE3760688D1 (en) 1989-11-09
FR2603083B1 (en) 1988-10-28
EP0258114A1 (en) 1988-03-02
FR2603083A1 (en) 1988-02-26

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